Turbine flowmeter



Nov. 7, 1967 TENHQ S ET AL 3,350,938

TURBINE FLOWMETER 5 Sheets-Sheet 1 Original Filed May 5, 1960 EN NNN @NM5 mm o N W L mm m Pig in mm 0Q mm mm W Howard E.Riflenhouse ATTORNEYS 7,1967 H. E. RITTENHOUSE ET AL 3,35

TURBINE FLOWMETER Original Filed May 5, 1960 3 Sheets-Sheet 2 INVENTORSSherman L. Wood Howard E. Riflenhouse H. RI'E'TENMOU5E ET AL 3,350,938

TURBINE FLOWMETER Nov. 7, R967 5 Sheets-Sheet 3 Original Filed May 5,1960 x \WV INVENTOR5 Sherman L. Wood Howard ERittenhouse Bam WMATTORNEYS N: mm. a m m L \M 1v wt 02% z x WV 3. 3 8., mma mmi 1w wt wowwow 8N Q8 ON United States Patent 3,350,368 TURBINE FLOWMETER Howard E.Rittenhouse and Sherman L. Wood, Stateshoro, Ga, assignors to RockwellManufacturing Company, Pittsburgh, Pa., a corporation of PennsylvaniaOriginal application May 3, 1960, Ser. No. 26,502, now Patent No.3,182,504, dated May 11, 1965. Divided and this application Apr. 1,1965, Ser. No. 444,700

Claims. (til. 73-231) This application is a division of application Ser.No. 26,502, filed May 3, 1960, for Fluid Meter, now Patent No. 3,182,504issued on May 11, 1965.

The present invention relates to turbine meters and more particularly toimprovements in such meters.

The present invention generally contemplates the provision of a specialturbine meter for accurately metering and recording the flow of fluidsand basically consists of a flow responsive metering turbine elementdisposed in a tubular housing which is adapted to be coaxially installedin a pipeline in the path of fluid flowing through the pipeline.

in meters of this type, the housing'is usually flanged or otherwisesuitably fixed to the pipeline containing the fluid to be metered. Thesepipelines are often of long length and of relatively large diameter andare often subject to extreme temperature and pressure variations. Thepipe stress resulting from changing temperature and pressure conditionsgives rise to complex problems of elasticity, moments and forces whichcause deformation of the pipeline and also of the meter housing. As aresult, the nudesirable stresses which are established and transmittedto the component metering parts, bind the operative metering partsagainst friction free movement, thereby creating a drag of varyingunpredictable magnitude on the metering turbine. As a consequence,uncompensated metering inaccuracies result from the changing temperatureand pressure conditions.

To overcome these difficulties, the present invention contemplates theprovision of a liner assembly having two cantilever supported shells,coaxially mounted in the meter housing and effectively floatinglysupporting the moving metering elements such that deformation of themeter housing does not cause axial deformation of the liner assembly ormovement thereof relative to the blades of the turbine rotor.

The present invention further contemplates a more compact, efficientlyorganized, and repairable turbine meter wherein the assembly anddisassembly of the component metering parts is easily and quicklyfacilitated. In accord with the present invention, the principalcomponent meter drive train parts serving to drive the meter register inresponse to flow of fluid through the blades of the metering turbine mayall be made so that the same component parts can be assembled in anysize meter within a given range, thereby facilitating readyinterchangeability of these drive components from one size meter toanother. This also permits higher volume production of theseinterchangeable components with resultant lower unit manufacturing cost.These component meter drive parts are compactly assembled as a unit sothat replacement of these parts as a unit can be readily accomplished.

In further accord with the present invention, the meter housing is madeup of two coaxial housing sections each having axially opposed endflanges which are generally similar to standard weld neck flanges usedin connecting sections of pipe and on intermediate pipe section. Theaxially adjacent flanges on each housing section are connected togetherto form a continuous enclosure of tubular configuration for theoperative meter parts. In order to safely withstand different ranges ofline fluid pressures, the wall thickness of the meter housing is variedand rated for one of a series of standard pressures associated with agiven nominal pipe size. Generally, it is the practice to vary theinternal diameter of such flanges on pipe sections for pipe sizes over12 inches in order to obtain a desired wall thickness for a givenpressure rating. By this standard practice, it will be appreciated thatcorresponding changes in the dimensions of the operative meter parts andthe inner liner assembly would be required in order to maintain thedesired clearances around the rotor blades and also to maintain theproper magnitude of flow area through the meter for obtaining optimumfluid velocities.

In the present invention, however, the diameter of internal flangesurfaces which serve to supportingly interflt regions on the inner linerassembly is maintained constant for the various pressure ratings of agiven pipeline size and irrespective of variations in the housing wallthickness. As a result, the same liner assembly for a meter of givennominal pipe size is usable with any one of a series of housings havinga variety of wall thicknesses and corresponding pressure ratings.

One advantage of the foregoing construction resides in the eliminationof the necessity for manufacturing different liner assemblies of varyingdimensions to correspond to the various internal pressure ratingdiameters of a pipeline for a given nominal pipe size. As a consequence,the number of replacement parts required to be stocked are reduced andthe same liner for a given nominal pipe size is interchangeable inmeters of differing pressure ratings. Thus, the dimensions of theoperative parts of the meter and the clearances between the meter partsproviding for passage of line fluid can be accurately maintainedirrespective of changes in the internal pipeline diameter foraccommodating different line fluid pressures. By means of this specialstructure providing for accurate fluid passage dimensions, the velocityof the line fluid flowing is accurately maintained within prescribedlimits and the tendency of line fluid to leak around the meter rotorwithout passing through the blades thereof is substantially reduced,thereby increasing the overall. accuracy of the meter.

Accordingly, a primary object of the present invention resides in theprovision of a turbine meter having a novelly supported and easilyassembled] turbine rotor.

Another object of the present invention is to provide a novel turbinemeter wherein component meter parts which are interchangeable indifferent size meters are mounted for assembly and disassembly as aunit.

Another object of the present invention is to provide a turbine meterhaving a tubular housing and a fluid flow responsive turbine rotordisposed in the housing wherein a special tubular structure supportingthe turbine rotor is novelly supported on bearing surfaces formed by theinterior wall of the housing such that deformations of the housing donot cause the tubular structure to deform or axially shift relative tothe blades of the rotor.

A further object of the present invention is to provide a measuringinstrument capable of accurately measuring rates of flowing fluid andhaving an instrument mechanism mounted in a thermally expansible andcontractible housing which is subject to deformation wherein a novelsupport structure rigidly supporting the instrument mechanism in apredetermined relation to the interior of the housing isolates themechanism from stresses induced in the housing by expansion andcontraction of the housing or by deformation of a pipeline to which thehousing may be connected.

A more specific object of the present invention is to provide a noveltubular turbine meter support shell composed of a pair of coaxiallyabutting axially elongate an- 0 nular members which are independentlycircumferentially positioned and anchored in separable coaxiallyadjacent (a housing sections along adjacent cylindrical surfaces inbearing contact with the interior of their respective housing sectionswherein the surfaces are axially spaced from regions Where at least oneof the annular members support the fluid flow responsive element of theturbine meter.

Still a further object of the present invention is to provide a novelturbine meter having a tubular housing, a fluid guide structure withinthe housing defining a venturi of hollow form and including coaxialupstream and downstream diffuser sections each having an outer shell anda central core, a turbine rotor journalled on the core of one of thesections with its blades disposed across the annular flow passagedefined by the sections wherein the section shells are secured to andsupported by the housing solely at their axially adjacent ends andwherein the cores are secured to and supported by the shells at theaxially remote end regions of the shells opposite from their adjacentends.

A further object of the present invention is to provide a novel annulartubular support structure for an axial flow turbine meter wherein thesupport structure is disposed coaxially in a tubular housing and issupported by an internal bearing surface formed on the internal wall ofthe housing at a predetermined region that is axially spaced from theposition at which the support structure supports the flow fluidresponsive element of the turbine meter.

Another object of the present invention is to provide a turbine meterhaving a hollow housing wherein a special hollow turbine rotor hubmember is rotatably mounted concentrically in the housing on a hollowspindle support member which is supported in cantilever fashion from thehousing and through which a shaft freely extends and has a portionprotruding beyond the free end of the tubular support which is drivinglyconnected to the hub member.

Still another specific object of the present invention is to provide anovel turbine meter having a tubular housing adapted to be axiallyinstalled in a pipeline, a fluid guide structure within the housingdefining a venturi of hollow form and including coaxial upstream anddownstream diffuser sections having coaxially mounted cores, a turbinerotor mounted on a hub which is journalled on the core of one of thesections with its blades disposed across the annular flow passagedefined by the sections, a register mechanism for recording the flow offluid through the turbine rotor blades and a drive train connecting therotor hub with the register mechanism including a magnetic couplinghaving a follower magnet assembly connected to the register mechanismand a drive magnet assembly connected to the hub by a shaft journalledby a spindle member removably mounted rigid with the meter housingwherein the shaft, the magnetic coupling and the spindle member areremovable and replaceable as a unit.

A further object of the present invention is to provide a novellubricant system for a turbine meter having a housing, a turbine rotorjournalled by bearing means in the housing, a drive traininterconnecting the rotor with a register and including a drive shaftwhich is drive connected to the rotor and which is journalled by bearingmeans wherein the bearing means for the shaft and rotor are lubricatedthrough a single fitting and a network of novelly arranged passages andchambers.

Further objects will appear as the description proceeds in connectionwith the appended claims and annexed drawings where:

FIGURE 1 is a longitudinal sectional view of a turbine meter embodyingthe principles of the present invention;

FIGURE 2 is an enlarged fragmentary longitudinal sectional view of themeter illustrated in FIGURE 1 and showing details of the rotor assemblyand connections therefor;

FIGURE 3 is an enlarged fragmentary longitudinal sectional view of themeter illustrated in FIGURE 1 and showing details of the drive traininterconnecting the turbine rotor with the meter register.

Referring now to the drawings in detail, and particularly to FIGURE 1,the turbine meter of the present invention comprises fluid guidestructure defining an upstream diifuser section 12 and a downstreamdiffuser 14 arranged in coaxial relation to define an annular flowpassage M in which is interposed a turbine rotor assembly 18. Thediffuser sections 12 and 14 are enclosed within a tubular housingstructure 29 formed in two sections 22 and 24 which are separable andprovided at opposite ends with suitable connection fittings such asflanges 26 and 28.

Housing section 22 comprises three parts designated 30, 32 and 34 joinedby annular welds 36 and 38 to form a generally tubular housing sectionwith a circumferentially apertured bolt flange 26 at one end and afurther circumferentially apertured bolt flange 40 at the other end.Housing section 24 is similarly formed of three parts 42, 44 and 46similarly joined by annular welds 48 and 50 to form a generally tubularhousing section with circumferentially apertured bolt flange 28 at oneend and a circumferentially apertured bolt flange 52 at the other end inopposed aligned relation with the bolt flange 40 of housing section 22.The housing sections 22 and 24 are fixedly connected together in coaxialrelation by bolt and nut assemblies 54 extending through the alignedapertures of the flanges 49 and 52. A fluid tight seal is establishedbetween the flanges 40 and 52 by an axially compressed O-ring 56received in an annular recess 58 formed in the end face 60 of flange 52,the O-ring 56 being compressed between the axial end wall of recess 58and the opposed face 62 of flange 40. By this construction, acircumferential fluid tight seal is formed between flanges 40 and 52about the tubular opening through housing 20.

Fluid meters of the type disclosed herein may, in operation, wheninstalled in a pipeline, be subjected to a very wide variety oftemperatures both internally as a result of variations in temperature ofthe pipeline fluid and externally due to variations in the atmospherictemperature. For example, a meter installed in a desert location willeasily be subjected to a range of temperature variations well in excessof F. Pipe stresses resulting from these changing temperature conditionsgive rise to complex problems of elasticity, moments and forces whichcause longitudinal deformation of the pipeline. Since the pipeline isusually restrained against longitudinal movement at locations where themeter is installed in the line, the stresses which are created by thesevarying temperature conditions and which are not compensated for in thedesign of the pipeline, are transmitted to meter housing 20 throughflanges 26 and 28 with the result that the housing deforms tending tobind the operative parts of the meter against friction free movement andthereby creating a drag of varying unpredictable magnitude upon thefluid flow responsive element. As a consequence, the strains establishedby severe changes in the temperature of the fluid being metered or inthe surrounding ambient air temperature appreciably affect the accuracyof the meter.

Assembly of the meter in the pipeline presents a further problem in thatthe relatively small alignment stresses which are set up when the meterhousing 21) and pipeline (not shown) are lined up and pulled togetherduring construction of the pipeline, are hot compensated for and,consequently, affect the accuracy of the meter by deforming housing 20.

In addition to the temperature and alignment stresses in the pipeline,the housing 20 itself will be subjected to external and internalchanging temperature conditions and to varying internal fluid pressuresdepending upon the pipeline pressure. These varying conditions willcause the housing 20 to expand and contract with consequent deformationof the component parts of the meter. In meters of the type heretoforeavailable, these variations in the size of the external housing,resulted in varying stress applied to the internal components of themeter providing a further drag upon the fluid flow responsive elementvarying with these conditions and resulting in metering inaccuracies.

The present invention overcomes these difficulties by, in effect,floatingly supporting the moving metering elements within the housing 20and isolating these elements from the stresses resulting from pipelinedeformation and from variations in the size of the housing 20 resultingfrom expansion and contraction thereof. The manner in which this isachieved will become apparent presently.

The upstream diffuser section 12 comprises an outer annular shell 64 andan inner hollow core 66, the core 66 being supported coaxially withinthe shell 64 by a plurality of fluid guide vanes 68, each lying in aplane passing through (i.e., including) the axis of the core 66 and theshell 64 and being secured to shell 64 by suitable machine screws 70 andto the core 66 by suitable machine screws 72. The shell 64 is providedat one end with an external radially offset annular flange 74 which, asassembled in the factory, snugly interfits in piloting relation with aradially outwardly offse't cylindrical surface 76 formed coaxially inthe end of upstream housing section member 34.

As is best seen in FIGURE 2, the circumferential position of shell 64within the housing section 22 is established by the cooperation of anaxially extending slot 78 formed in the upstream end of the annularflange 74 and a dowel pin 80 extending through an aperture 82 formedradially through the housing member 34. The diameter of dowel 80 isequal to the circumferential width of slot 78 so that when dowel 80 isin engagement with slot 78 as illustrated in FIGURE 2, the shell 64 isrestrained against rotation relative to the housing member 34 andhousing section 22. The shell 64 is anchored axially within member 34 bya machine screw 84 threaded through a radially extending threadedaperture 86 in member 34 and projecting at its end into a radiallyextendiing recess 88 in the radially outer cylindrical face 90 of flange74 of shell 64. An O-ring 92 is compressed between the head of screw 84and the opposed face of member 34 to prevent loss of fluid through theaperture 86.

As will be apparent from FIGURE 1, with the exception of the flange 74,the shell 64 extends through the housing section 22 in radially spacedrelation so that while contraction or deformation of the housing section22 will subject the flange 74 to circumferential forces, shell 64 is,along the remainder of its length, free of any axial deformationinhousing section 22 and of any externally appliedcircumferential forces.With the supporting cylindrical surface of shell flange '74 near thecenter of the meter assembly, housing section 22 can be slightlydeformed without causing movement of shell 64 with respect to rotor 18.

The vanes 68 by which the core 66 is supported within shell 64 arelocated at the end of shell 64 opposite the flange 74 so that thesevanes 68, while extending approximately one half the longitudinal lengthof shell 64 are subjected to a minimum amount of displacement resultingfrom forces on flange 74 upon the contraction or deformation of thehousing member 34. The vanes 68 are secured to the core 66 substantiallyat the center of the longitudinal length of core 66 and as will becomeapparent presently, the moving components disposed within the hollowcore 66 are supported from the ends of core 66 so that compressive anddeformation forces transmitted through vanes 68 are transmitted to theportion of core 66 well removed from the regions at which th movingparts are supported.

As is apparent from FIGURE 1, the core 66 is substantially conical inform having an insert stepped shank plug 96 at its upstream apex and atransverse end plate 5&8 at its downstream base and fixed to the mainportion thereof by a screw 100. The core 66 houses a viscositycornpensating device of the viscous drag drum type operative upon theprinciples disclosed in detail in copending application Serial No.795,755, now Patent No. 3,248,945, to which reference is made in theevent a more detailed description than that herein given is found to benecessary to a complete understanding of this aspect of the invention.The viscosity compensator comprises a fixed hollow member 102 having aninlet chamber 164 and a cyclindrical drum chamber 106 connected in fluidcommunication through a passage 108. The fixed member 162 is disposedcoaxially within the core 66, being sup ported upon the base end wall 98at its downstream end and upon the shank of insert plug 96 at itsupstream end. A drum 110 is journalled coaxially within the cylindricaldrum chamber 106 by an antifriction bearing assembly 112 supported atthe center of the wall 98 and by a further antifriction bearing assembly114 on the end wall 116 of the drum chamber 106 defined by member 102.The drum 110 is cylindrical in form and has an external diameterslightly less than the internal diameter of the cylindrical chamber 166so that the external surface of drum 111) rotates in closely spacedrelation to the internal cylindrical surface of the drum chamber 166. Asis explained in detail in said copending application Serial No. 795,755,now Patent No. 3,248,945, a small amount of fluid is tapped from thepipeline upstream of the meter and fed through a suitable strainer tothe viscosity compensator.

In the present invention, the strained fluid tapped upstream of themeter is fed through an inlet fitting 118 into a pipe 120 which extendsthrough an aperture 122 in the core 66 and opens at its discharge endinto the chamber 164. Fluid flows from the chamber 104 through the inletopening 108 into the chamber 166 where it flows between the cylindricalexternal surface of the drum 110 and the internal cylindrical surface ofthe chamber 166 to the downstream end of chamber 166 for dischargethrough an outlet passage 124 for-med in member 98 for discharge intothe annular channel 16 upstream of the rotor 18. Pipe 120 is providedwith fluid tight universal end fittings of conventional form permittinglimited relative axial displacement between the housing section 22 andthe fixed member 162 but retaining the fluid tight connections at theopposite ends of pipe 126 without inducing stress within pipe 120. Alubricant supply duct extending between a conventional lubricant fitting128 fixed to the outside of member 32 permits introduction of lubricantto the bearing 114 for the drum 110.

As is shown in FIGURE 1, the internal diameter of shell 64 is preferablyequal to the internal diameter of the member 30 and the inlet portion ofmember 32 so that shell 64 for practical purposes constitutes an equaldiameter extension of the pipeline and inlet portion of the housingsection 22.

The annular space 136 between the exterior of shell 64 and the largediameter portion of member 32 is, as will become apparent, a dead spacehaving no fluid outlet at its downstream end so that there is notendency for line fluid to flow into the space 130. As a consequence,space performs a further function in that it provides substantiallyequal fluid pressure on opposite sides of the shell 64 so thatvariations in pressure of the line fluid will not produce any variationsin the stress transmitted through vanes 68 to the core 66. Likewise, thefluid pressure is substantially equal both internally and externally ofcore 66 since the interior of core 66 is open to line fluid pressurethrough the large opening 122 through which the pipe 120 passes and thelarge opening 129 through which the lubricant pipe 126 passesv Withcontinued reference to FIGURES 1 and 2, the downstream diffuser section14 comprises an outer annular shell 146 coaxial with shell 64 and aninner core 142, the core .142 being supported coaxially within shell 140by a plurality of guide vanes 144, each lying in a plane passing throughthe axis of core 142 and shell 140 and being secured to shell 146 bysuitable machine screws 146 and to core 142 by suitable machine screws148. Vanes 144 are in equiangularly spaced relationship about the axisof core 142 and shell 140.

Shell 140 is structurally similar to shell 64 and has an internal borediameter equal to that of shell 64 and an annular radially offset endflange 150 forming a cylindrical outer surface 151, the outer diameterof which is equal to that of flange 74. Flange f axially abuts flange 74and snugly interfits in piloting relation with an external radiallyoutwardly offset cylindrical surface 152 which is formed coaxially inthe end of downstream housing section member 42 and which is of the samediameter as cylindrical surface 76. By this structure, the assembly ofshells 64 and 140 forms a substantially continuous uniformly diameteredinternal cylindrical surface in concentric spaced relationship withcores 66 and 142.

The means for circumferentially positioning and anchoring shell 140 isthe same as that provided for shell 64 and since like reference numeralsare used to identify like elements, no further description of this meanswill be given.

With continuing reference to FIGURES 1 and 2, the axial length of flange150 is greater than that of flange 74 and is of such magnitude to extendaxially on both sides of recess 58 and to concentrically surround rotor18 which is provided with a set of equiangularly spaced apart blades154. O-ring 56 is compressed against 62 of member 20 by surface 58 ofmember 42 while being positioned by outer peripheral surface of flange150 thereby preventing leakage of line fluid between the axiallyabutting end faces 60 and 62 of members 40 and 52.

The internal periphery of flange 150 is radially outwardly offset fromthe internal cylindrical peripheral wall surface 156 of shell 140 andforms with the planar end face of flange 74 an annular recess 158 whichis proportioned and formed to receive the outer ends of rotor blades154. Recess 158 functions to establish fluid turbulence between blades154 and shell 140. The fluid turbulence thus created effects a positiveturbulent seal around the rotor blades 154 to substantially reduce theleakage of fluid which would otherwise escape without being meteredthrough the running clearance between blades 154 and shell flange 150.

By disposing the blades 154 of rotor 18 completely axially between theends of shell 141), the possibility of causing damage to blades 154 whenhousing sections 22 and 24 are separated or when shell 64 is removed issubstantially precluded.

As is shown in FIGURE 1, the internal diameter of shell 140 ispreferably equal to the internal diameter of member 46 so that member 46constitutes an equal diameter extension of the pipeline and outletportion of housing section 24. As a consequence, an annular passagewayformed by cores 66 and 142 with shells 64 and 144) and housing members30 and 46, has a substantially uniform outer periphery free of exposedpockets that would cause eddy currents to be established and therebydisturb the flow of fluid through rotor 13.

The annular space 159 formed between the exterior of shell 140 and thelarge diameter portion of member 44 is a dead space similar to space 130and performs the function of equalizing the fluid pressure on oppositesides of shell 140 so that variations in pressure of the line fluid willnot produce variations in the stress transmitted through vanes 144 tocore 142. Likewise, the fluid pressure is equal both internally andexternally of core 142 as the interior of core 142 is open to line fluidpressure through openings 160, 161 and 162.

By the foregoing two-piece shell structure, it will be appreciated thataxial deformation of one housing section does not materially affect theshell in the adjacent housing as shells 64 and 140 are independentlyanchored and circumferentially positioned to their respective housingsections 22 and 24.

When the meter is installed in a pipeline, it is standard practice toanchor the meter preferably at a point midway between flanges 26 and 28.Thus, axial deformation of the pipeline (not shown) in which the meteris installed will cause a proportional deformation in housing 20. Bymounting shells 64 and in cantilever fashion, the axially opposed endsof shells 64 and 140 are free to float in housing 20 and the shellsconsequently are not deformed by stresses creating deformation ofhousing sections 22 and 24. As a result, the cores 66 and 142 which aresupported at the free floating end portions of shells 64 and 141) aremaintained in position relative to the center of housing 20 betweenflanges 40 and 52 and blades 154 and are not shifted or deformed bystress deformation of housing 20. Thus, the meter components supportedin cores 66 and 142 are effectively isolated from stresses resultingfrom deformation of housing 20. The accuracy of the meter, therefore,remains unaffected by the stresses set up by pipeline deformation whichis transmitted to deform housing 20 and which would otherwise cause therotating components of the meter to drag with increased friction.

In the meter of the present invention, it will be appreciated that it isnecessary to vary the thickness of housing 20 in accordance with themeter pressure rating so that the housing can withstand the rated fluidline pressures to which the meter is to be subjected. In the past, ithas been the practice in construction of piping and flanges to vary theinside diameter of the pipe or the flange particularly for sizes over 12inches in order to obtain the desired wall thickness that will safelywithstand the fluid pressure for which the piping and connecting flangesare rated.

In varying the inside diameter of piping and flange components ofhousing 20 and particularly the internal recessed diameters of flangemembers 34 and 42, the accuracy of the meter when constructed withoutthe inner liner assembly composed of shells 64 and 140 is seriouslyimpaired. To this end it will be appreciated that slight variations inthe internal diameter of the walls forming recess 158 wouldsubstantially reduce the effectiveness of the turbulent seal formedbetween the tips of rotor blades 154 and the bottom wall surfaces ofrecess 158 and, consequently, would cause appreciable meteringinaccuracies. It is essential in a meter according to the presentinvention that magnitude of the clearance between the tips of blades 154and the bottom wall surface of recess 158 be accurately maintainedwithin extremely close tolerances in order to achieve the highlyaccurate measurements obtainable with this meter.

Without the inner liner assembly composed of shells 64 and 140, it isequally clear that variations of the internal diameter of housing 20forming the outer wall of the annular flow passage defined by diffusersections 12 and 14, will cause corresponding variations in the velocityof the fluid flowing through rotor blades 154 from the normal velocityfor given conditions of temperature pressure, viscosity, etc. As aconsequence, the extremely high accuracy normally obtainable with themeter of the present invention is undesirably affected. If the meter isto function properly and provide the highly accurate measurements forwhich it is designed, it is essential to maintain the velocity of thefluid flowing through the annular venturi within extremely closepredetermined limits relative to the norm.

In order to overcome the difficulties established by the necessity ofvarying the wall thickness of housing 20 in accord with the pressurerating of the meter, the present invention contemplates the provision ofa meter housing wherein the diameters of internal surfaces 76 and 152 offlange members 34 and 42 are the same for all the different housing wallthicknesses associated with the various meter pressure ratings of agiven nominal pipe size. By means of this construction, the same innerliner assembly composed of shells 64 and 140 can be interchangeablyassembled in meter housings having a variety of thicknessescorresponding to a given series of pressure ratings. Thus, it will beappreciated, that the turbulent seal clearance between rotor blades 154and the bottom wall of recess 15% is not affected by variations in thethickness of the component parts of housing sections 22 and 24.Furthermore, by facilitating the use of identically dimensioned shells64 and 140 for the various meter pressure ratings of a given nominalmeter size, variations in the internal diameter of housing members 30,32, 44 and 46 to obtain the necessary wall thickness that would safelywithstand the rated pressure, do not aflect or cause variations in thevelocity of the line fluid flowing through the venturi formed by shells64 and 140 and cores 66 and 142. As a consequence, the dimensions of theturbulent seal clearance and of the venturi flow passages can easily andaccurately be maintained within the extremely close limits necessary toachieve the high metering accuracy attainable with the meter.

It is equally clear, that by constructing shells 64 and 140 with equaldimensions for interchangeable use in the different pressure ratedmeters of a given nominal size, high volume production is facilitatedwith resultant lower manufacturing costs.

As is apparent from FIGURES 2 and 3, rotor blades 154 are mounted on arim 170 which is supported coaxially in housing section 24 by aplurality of equiangularly spaced generally radial extending spokes 172.In accord with the present invention, spokes 172 together with rim 170and blades 154- are mounted as a unit on a hollow axle hub 174 having athrough bore 175 and axially opposed annular end flanges 176 and 178 towhich the inner ends of spokes 172 are alternately secured.

As best shown in FIGURES 2 and 3, hub 174 is mounted for rotation on anelongated hollow axle spindle 180 in concentric spaced apart relationthereto by means of axially spaced apart antifriction bearing assemblies182 and 184. Bearing assembly 182 is axially retained in place onspindle 180 between a collar nut 185 secured onto a threaded terminalfree end section 186 of spindle 180 and an annular spacer 188 whichaxially abuts the inner races of both bearing assemblies 182 and 184.

Bearing assembly 184 has its inner race mounted on spindle 180 and hasits outer race fitted into a counter bore 190 formed in the right-handend of hum 174 as viewed from FIGURES 2 and 3.

The inner race of bearing assembly 184 is axially confined betweenspacer 188 and a slinger ring 192 which is axially positioned betweenthe bearing inner race and an axially facing annular shoulder formed byspindle 180. The outer race of bearing assembly 184 is axially confiinedbetween an annular shoulder 194 formed at the base of counter bore 190and a retainer ring 196 which is secured to hub 174 as by machine screws198.

With continuing reference to FIGURES 2 and 3, spindle 180 is cantileversupported from a transverse end plate 200 and is preferably formedintegral therewith. Plate 200 is fixedly secured to an annular flangeportion 202 of a support member 204 as by machine screws 206. Supportmember 204 is secured by screws 207 to a transverse partition wall 208of core 142 and has an intermediate shoulder section 210 providing anaxial cylindrical surface which interfits with piloting relation in anaperture 212 formed centrally in partition wall 208. By this rotorsupport structure, it will be appreciated :that rotor 18 is rotatablymounted on spindle 180 which is cantilever supported from end plate 208.

With continuing reference to FIGURE 2, support member 204 is providedwith a terminal cylindrical section 214 which axially extends into acompartment 216 formed by the interior wall surface of core 142 and byend plate 200 and which houses a magnetic drive coupling 218.

As will be explained in greater detail presently, coupling 218 comprisesa magnetic driving element 220 l which is magnetically coupled to amagnetic follower elemerit 222 through a non-magnetic tubular partition224 forming a static fluid seal therebetween as best shown in FIGURES 2and 3. Partition 224 is threadedly received in an axially extendingannular well 226 formed in a worm gear housing 228 and is maintained influid tight relation therewith by an O-ring 230 positioned in an annulargroove formed between partition 224 and housing 228. Housing 228 isprovided with an annular flange portion 232 fixedly secured tocylindrical section 214 by machine screws 234 and with an annular skirt236 substantially equal in diameter to the internal counter boreddiameter of cylindrical section 214 to be received in a fluid tightpilot fit therein.

By this housing structure, it will be appreciated that housing 228together with end plate 200 and cylindrical section 214 form a chamberwithin core 142 which is divided into two separate compartments 238 and240 by means of partition 224 and respectively containing drivingelement 220 and follower element 222. Diametrically opposed apertures232 formed radially in cylindrical section 214 connect the corecompartment 216 with the driving element compartment 238 to equalize thepres sures on both sides of support member 204. Since partition 224forms a fluid tight seal with housing 228, line fluid in corecompartment 216 is only allowed to enter compartment 238 and compartment240 is sealed fluid tight against entrance of fluid therein.

The follower element 222 drives a horizontal axially extending shaft 244journalled in an antifriction bearing assembly 246 which has its outerrace press fitted into a recess 248 formed at the base of wall 226. Aworm gear segment 250 is mounted on the right-hand end of shaft 244, asviewed from FIGURE 2, and constantly meshes with a worm wheel 252 fixedto a vertically extending shaft 254 which is coaxially aligned andadapted to be rotatably coupled to a register drive shaft 256.

As shown in FIGURE 3, shaft 254 is journalled at its lower end in anantifriction bearing assembly 257 mounted in a stepped bore 258 formedin gear housing 228 and at its upper end by an antifriction bearingassembly 259 received in a recess formed in an adapter piece 260 whichis fixedly secured to housing 228 by means of machine screws 261. Shaft256 is provided with an end portion 262 having opposed flat sides whichinterfit in a flat sided recess 263 formed in a coupling member 264 toprovide for a rotatable drive connection between shaft 256 and couplingmember 264 but permitting shaft 256 to be freely lifted clear ofcoupling member 264 for a purpose as will become apparent. Coupling 264is suitably fixed to the upper end of shaft 254 as be set screw 265.

As best shown in FIGURE 2, register drive shaft 256 extends freelythrough a rigid conduit 266 which is freely received through apertures267 and 268 formed respectively in shell and housing member 44, and coreaperture 161 and protrudes beyond housing section 24. Con duit 266 isprovided with fluid tight universal end fittings of conventional formwhich are respectively mounted in a housing fitting 270 and adapterpiece 260 thereby permitting limited relative axial movement betweenshell 140 and the fixed housing member 44 but retaining the fluid tightconnection without inducing stress in conduit 266.

As is clearly shown in FIGURE 2, shaft 256 protrudes beyond fitting 270for connection to a conventional mechanical register 271 and isjournalled at its upper end by means of an antifriction bearing assembly272 recessed in a register mounting plate 274 which is fixed to fitting270 by machine screws 276.

With reference now to FIGURE 3, the follower magnet assembly 222 ismounted in the sealed compartment 240 for coaxial rotation at one end bya stub shaft 278 which is journalled in an antifriction bearing assembly280. Bearing assembly 280 is disposed in a recess formed by the axiallyfacing end wall of partition 224. Follower 222 comprises a cylindricalplastic magnetic support 1 l 282 having diametrically opposed recessescut in the periphery thereof to receive cylindrical permanent barmagnets 284 and 286. Magnet support 282 is fixed to shaft 244 which iscoaxial with stub shaft 278.

The magnetic coupling driving element 220 consists of a rigid yoke 288preferably formed of stainless steel and having a pair of parallel armsformed with end faces that are planar and perpendicular to the axis ofrotation of coupling 218. A pair of permanent bar magnets 290 and 292abutting the planar end faces of the arms of yoke 288 are held rigidlyin place with their longitudinal axes extending parallel to the yokerotational axis by means of U-shaped sleeves 293 and 293a whichcoextensivcly fit over magnets 200 and 292 and the arms of yoke 288 andwhich are fixed thereto as by soft soldering to hold each magnet rigidlyin place in abutting end-to-end relationship with the respective endfaces of the yoke arms. The axes of magnets 290 and 292 are equallyspaced from the rotational axis of yoke 288 in parallel relationshipthereto and are disposed in surrounding relationship to the tubularpartition 224. Thus, drive magnets 290 and 292 are rotatable in acircular path outside of partition 224 in concentric relation to therotational path of follower magnets 284 and 286 inside of partition 224,the partition being disposed concentrically between the two paths ofmagnet rotation.

In order to rotate yoke 288 in response to fluid flow, a drive shaft 294is fixed in a bore formed in the cross piece of yoke 288 in coaxialrelationship with shaft 244. Shaft 294 is journalled at its right-handend, as best viewed from FIGURE 3, by an antifriction bearing and sealassembly 296 and extends coaxially through the axial bore 298 of spindle180, having a portion extending beyond the left-hand end face of thespindle. Bearing as sembly 296 is received in an annular recess 299formed in end face 300 of end plate 200. The outer race of bearing 296is confined between an annular retainer 302 which is fixed to plate 200as by machine screws 304 and the bottom annular wall of recess 299. Theinner race of bearing 296 is axially clamped between a retainer ring 306fixed to shaft 294 and an axially facing abutment shoulder formed by anenlarged diameter portion 308 of shaft 294, the opposite axially facingabutment surface of which is in bearing contact with the cross piece ofyoke 288.

With continued reference to FIGURE 3, the left-hand end of shaft 294extending beyond spindle 180, axially and freely protrudes into a bore310 formed in a hub cap member 312 and is fixedly secured therein bymeans of a pilot fit and diametrically opposed set screws 314. Hub cap312 is provided with a terminal axially extending cylindrical skirt 316which is received, with a pilot fit, in bore 175 of axle hub 174 andwith a flat sided annular flange portion 318 adjacent skirt 316. Flangeportion 318 axially abuts the planar end face of axle hub 174 and isfixed thereto as by machine screws 320.

As best shown in FIGURES 2 and 3, hub cap 312 is provided with a counterbore 322 which is formed coaxial with bore 310 and which receives theshank portion of a coupling 324 with a non-rotatable press fit. Coupling324 is fixedly secured into the free end of a stub shaft 326 coaxiallyfixed to drum 110 and journalled in bearing 112.

By this structure, it will be appreciated that shaft 294 is rotated inresponse to fluid flow through turbine blades 154 and is concomitantlyretarded from rotating by the viscous action of the line fluid flowingover drum 110 as hereinbefore explained. Rotation of shaft 294 isimparted to yoke 288 of magnetic coupling 218. The relation between thedriving magnets 290 and 292 and the follower magnets 284 and 286 is suchthat, as shaft 204 is rotated, the follower assembly 222 will be causedto rotate either by magnetic attraction of the follower magnets 284 and286 to the driving magnets 290 and 292 or by repulsion of the followermagnets 284 and 286 from the driving magnets 290 and 292, depending uponthe relative orientation of the poles on the magnets. Rotation of thefollower 222 imparts rotation to shaft 244 and worm 250 which is fixedto the end thereof ex-teriorly of bearing 246 and which meshes with wormwheel 252. As a consequence, rotation is imparted to shaft 254 which iscoupled to register shaft 256 as previously described.

From the foregoing description, it is apparent that partition 224 andhousing 228 seals compartment 240 from fluid flowing through apertures242 into compartment 238 so that the rotary motion of follower 222 istransmitted to register shaft 256 without the use of any dynamic fluidseals such as stuffing boxes and thus provides a fluid tight registerassembly.

It is further apparent from the foregoing description that spindle 180,shaft 294, support 204, magnetic coupling 218, housing 228, shaft 254,coupling 264 and adapter piece 260 are all removable as a unit throughaperture 212 of core wall 203 and constitute a drive train assembly 329for rotating register shaft 256 in response to fluid flow through blades154. The removal of drive train assembly 329 is readily accomplished byseparating housing sections 22 and 24 to provide access to rotorassembly 18. Set screws 314 securing drive shaft 294 to hub cap 312 areloosened and screws 320 are removed to disconnect hub cap 312 from axlehub 174. Rotor assembly 18 including blades 154, spokes 172 and axle 174are then preferably removed as a unit by removing nut 185 to insureagainst damage to blades 154 while removing the drive train. Registerhousing 271 and register base plate assembly 274 is then removed toprovide access to conduit 266 and shaft 256. Both conduit 266 and shaft256, being axially retractable, are lifted clear of adapter piece 260.By now removing screws 207, the components of drive train 329 areremoved as a unit through aperture 212.

The foregoing component parts of drive train 329 which are removable asa unit, and also axle hub 174, hub cap 312 and nut 185 are all made sothat the same component parts can be assembled in any size meter withina preferred 10 inch to 16 inch range. As a consequence, drive train 329is interchangeable in the various sizes of meters and the necessity ofmanufacturing different size component parts for each meter size iseliminated. In addition, this meter drive train may be removed as asingle unit from a meter of one size and assembled in a meter of adifferent size. Thus, the only operative metering components that varyin size according to the pipe diameter size of the meter are theviscosity drum 110, the diffuser sections 12 and 14 and the blades 154,rim and spokes 172 of rotor assembly 18.Thus, the manufacture ofdifferent sizes of meters particularly within the 10 inch to 16 inchrange is easily facilitated and the problems involved in stocking partsfor the various sizes of meters is greatly simplified in addition tofacilitating mass production with resultant lowering of manufacturingcosts.

In order to lubricate bearings 296, 182 and 184, a lubircant fitting 330is provided, as shown in FIGURE 1, and is fixed to housing section 24 inupstanding relationship at an angle of approximately 45 degrees from avertical plane passing through the longitudinal axis of the meter.

Lubricant introduced into fitting 330 is supplied by pressure through adownwardly inclined pipe 332 which interconnects fitting 330 with anaxially extending passage 33 formed in wall 208 of core 142 as bestshown in FIG- URE 3. Passage 333 is axially aligned with an axialpassage 334 formed in support member 202 which is intersected by aradially extending channel 335. Channel 335 communicates with acircumferential groove 336 formed in the surface 338 of the portion ofend plate 200 interfitting with the axial bore of member 202. By thisconstruction support member 202 may be removed Without disconnectingpipeline 332.

Lubricant supplied to groove 336 is furnished to a lubricant well 340formed coaxial with spindle bore 298 at the base of recess 29.9 by meansof at least one radial passage 342 connected at its outer end to groove336 and at its inner end towell 340. By this passageway construc tion,lubricant introduced into well 340 is forced into recess 299 andlubricates bearing 296. Lubricant is also forced from well 340 into bore298 between the peripheral wall of bore 298 and the outer periphery ofshaft 294. The lubricant passing through bore 298 flows into a chamber344 formed by hub cap 312 and axle hub 174 and then into bore 175 tothereby facilitate lubrication of bearings 182 and 184.

From the foregoing description, it will be appreciated that only asingle fitting 330 and one connecting line 332 is required to lubricatebearings 182, 184 and 296 serving to journal axle hub -174 and shaft 294respectively and that the foregoing component drive train parts whichare assembled and disassembled in the meter as a unit, may be removedwithout necessitating the disconnection of lubricant line 332.

The invention may be embodied in other specific forms without departingfrom the spirit or essential characteristics thereof, The presentembodiment is therefore to be considered in all respects as illustrativeand not restrictive, the scope of the invention being indicated by theappended claims rather than by the foregoing description, and allchanges which come within the meaning and range of equivalency of theclaims are therefore intended to be embraced therein.

What is claimed and desired to be secured by United States LettersPatent is:

1. A fluid flow meter comprising a pair of axially aligned, tubularaxially spaced apart housing sections, means rigidly joining saidhousing sections together comprising a pair of matching flanges formedseparately of and rigidly fixed to respective ones of said housingsections, said flanges extending axially between opposed ends of saidhousing sections to define therewith a continuous, tubular shapedhousing, a liner coaxially received in said housing and seated only onthe internal periphery of at least one of said flanges to be supportedthereby, a core coaxially mounted within and supported from said liner,said core and said liner defining a fluid flow channel of annular crosssection, and a rotor rotatably supported on said core to be driven byfluid flow through said channel, the diameter of the internal peripheryof said at least one flange remaining constant regardless of variationsin the wall thickness of said at least one flange to accommodatedifferent fluid pressures for a given nominal pipe size.

2. A fluid flow meter comprising a pair of axially aligned, tubular,axially spaced apart housing sections, means rigidly joining saidhousing sections together comprising a pair of matching, abuttingflanges rigidly fixed to respective ones of said housing sections andextending axially between opposed ends of said housing sections todefine therewith a continuous, tubular shaped housing, a liner assemblyof elongated tubular configuration coaxially received in said housingand seated only on the internal peripheries of said flanges to besupported thereby, said liner assembly being rigid at least in theregion where it seats on the internal peripheries of said flanges, afluid guide core structure mounted coaxially within and fixed to saidliner assembly, and a metering rotor rotatably supported by said corestructure, said core structure cooperating with said liner to define afluid flow channel of annular cross section for axially directing motivefluid into, through, and beyond said rotor to impart drive torque tosaid rotor.

3. The fluid flow meter defined in claim 2 wherein said liner assemblycomprises a pair of separable, separately formed, axially aligned linersections abutting along a i4 radial interface that is axially offsetfrom the radial interface between said flanges.

4. The fluid flow meter defined in claim 3 comprising a resilientsealing ring engagingly surrounding one of said liner sections, saidsealing ring being axially confined between said flanges whereby leakagealong the periphery of said one liner section and between said flangesis prevented.

5. The fluid flow meter defined in claim 3 wherein said liner sectionsare formed at adjacent ends with radial outwardly offset portions havingsmooth cylindrical peripheries surrounded by and interfittingly seatedagainst the internal peripheries of said flanges.

6. The fluid flow meter defined in claim 5 wherein said offset portionscooperate to define an annular inwardly opening recess radially aligningwith and circumferentially surrounding said rotor.

7. The fluid flow meter defined in claim 5 wherein said flanges are soformed and arranged as to define an inwardly opening recess receivingsaid offset portions.

8. The fluid flow meter defined in claim 5 comprising means on saidhousing for axially retaining said liner sections in abutment with eachother.

9. The fluid flow meter defined in claim 2 wherein said liner assemblycomprises a pair of liner sections seatingly supported at their adjacentends on the internal peripheries of said flanges and extending axiallyin opposite directions in radially inwardly spaced relation to saidhousing section to define therewith annular spaces opening into theinterior of said housing in axially, oppositely facing directions forallowing line fluid to be metered to apply pressure to both the outerand inner peripheries of said liner sections.

10. A turbine meter insert assembly adapted for insertion in operativerelation in any of a series of centrally separable external turbinemeter housings of similar central internal cross section for differingmetering applications, said insert assembly comprising an upstreamdiifuser section and a downstream diffuser section, each of saidsections comprising a tubular shell and a coaxial core, said sectionswhen disposed in axially aligned relation defining a passage of annularcross-section through which fluid flows for metering, a peripherallybladed turbine metering rotor journalled coaxially on the core of one ofsaid sections with its blades disposed in said passage so that axialmovement of fluid through said passage will impart rotation to saidrotor, a drive train in the core of said one section having its inputdrive connected to said rotor and a rotatable output member, the coreand shell of said one. section having aligned apertures therein inalignment with said output member and through which a drive shaft canextend and be drive coupled to said output member, the adjacent ends ofsaid section shells having externally enlarged portions definingtogether an external cylindrical piloting surface and axially spacedshoulders whereby the radial and axial positions of said assembly withinany housing of such a series may be established, means in the core ofthe other of said sections defining an internal surface of revolution ofpredetermined axial extent, a drum journalled within said surfacedefining means coaxial with said surface and having an external surfaceof revolution closely uniformly spaced from said internal surface ofrevolution, and means drive coupling said drum to said rotor, said othersection core and said surface defining means having means definingpassages at opposite ends of said drum permitting introduction of linefluid into the space between said surfaces of revolution and dischargeof line fluid from the space between said surfaces of revolution intosaid annular passage upstream of said turbine rotor, said surfaces ofrevolution coacting with the line fluid therebetween comprising aviscosity compensating device imposing a variable drag upon said turbinerotor continuously proportional to the viscosity of the fluid beingmetered.

(References on following page) References Cited UNITED STATES PATENTS2,772 8/ 1875 Great Britain. Chisholm 29-157 14,060 4/ 1852 GreatBritain. gascal 73231 X 728,132 11/1942 Germany.

rewer 73-231 04 333 1 19 8 Barteli k 73 231 X 1/ 5 Great Brltaln.

JAMES J. GILL, Acting P'rim'ary Examiner.

u at e a Taylor X Examiner. Kindler et a1 73194 10 EDWARD D. GILHOOLY,Assistant Examiner. Rittenhouse et a1 73-231 1 6 FOREIGN PATENTS

1. A FLUID FLOW METER COMPRISING A PAIR OF AXIALLY ALIGNED, TUBULARAXIALLY SPACED APART HOUSING SECTIONS, MEANS RIGIDLY JOINING SAIDHOUSING SECTIONS TOGETHER COMPRISING A PAIR OF MATCHING FLANGES FORMEDSEPARATELY OF AND RIGIDLY FIXED TO RESPECTIVE ONES OF SAID HOUSINGSECTIONS, SAID FLANGES EXTENDING AXIALLY BETWEEN OPPOSED ENDS OF SAIDHOUSING SECTIONS TO DEFINE THEREWITH A CONTINUOUS, TUBULAR SHAPEDHOUSING, A LINER COAXIALLY RECEIVED IN SAID HOUSING AND SEATED ONLY ONTHE INTERNAL PERIPHERY OF AT LEAST ONE OF SAID FLANGES TO BE SUPPORTEDTHEREBY, A CORE COAXIALLY MOUNTED WITHIN AND SUPPORTED FROM SAID LINER,SAID CORE AND SAID LINER DEFINING A FLUID FLOW CHANNEL OF ANNULAR CROSSSECTION, AND A ROTOR ROTATABLY SUPPORTED ON SAID CORE TO BE DRIVEN BYFLUID FLOW THROUGH SAID CHANNEL, THE DIAMETER OF THE INTERNAL PERIPHERYOF SAID AT LEAST ONE FLANGE REMAINING CONSTANT REGARDLESS OF VARIATIONSIN THE WALL THICKNESS OF SAID AT LEAST ONE FLANGE TO ACCOMMODATEDIFFERENT FLUID PRESSURES FOR A GIVEN NOMINAL PIPE SIZE.